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US7789069B2 - Check valve, and injector with hydraulic booster and check valve - Google Patents

Check valve, and injector with hydraulic booster and check valve Download PDF

Info

Publication number
US7789069B2
US7789069B2 US12/520,136 US52013608A US7789069B2 US 7789069 B2 US7789069 B2 US 7789069B2 US 52013608 A US52013608 A US 52013608A US 7789069 B2 US7789069 B2 US 7789069B2
Authority
US
United States
Prior art keywords
bore
valve
stop element
check valve
stroke stop
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Fee Related
Application number
US12/520,136
Other languages
English (en)
Other versions
US20100024774A1 (en
Inventor
Nestor Rodriguez-Amaya
Markus Leimser
Michael Stengele
Andreas Theurer
Christoph Butscher
Alexander Giehl
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Assigned to ROBERT BOSCH GMBH reassignment ROBERT BOSCH GMBH ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: GIEHL, ALEXANDER, STENGELE, MICHAEL, LEIMSER, MARKUS, RODRIGUEZ-AMAYA, NESTOR, THEURER, ANDREAS, BUTSCHER, CHRISTOPH
Publication of US20100024774A1 publication Critical patent/US20100024774A1/en
Application granted granted Critical
Publication of US7789069B2 publication Critical patent/US7789069B2/en
Expired - Fee Related legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K15/00—Check valves
    • F16K15/02—Check valves with guided rigid valve members
    • F16K15/04—Check valves with guided rigid valve members shaped as balls
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M47/00—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure
    • F02M47/02—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure of accumulator-injector type, i.e. having fuel pressure of accumulator tending to open, and fuel pressure in other chamber tending to close, injection valves and having means for periodically releasing that closing pressure
    • F02M47/027—Electrically actuated valves draining the chamber to release the closing pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M57/00—Fuel-injectors combined or associated with other devices
    • F02M57/02—Injectors structurally combined with fuel-injection pumps
    • F02M57/022—Injectors structurally combined with fuel-injection pumps characterised by the pump drive
    • F02M57/025—Injectors structurally combined with fuel-injection pumps characterised by the pump drive hydraulic, e.g. with pressure amplification
    • F02M57/026—Construction details of pressure amplifiers, e.g. fuel passages or check valves arranged in the intensifier piston or head, particular diameter relationships, stop members, arrangement of ports or conduits
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/02—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type
    • F02M59/10—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type characterised by the piston-drive
    • F02M59/105—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type characterised by the piston-drive hydraulic drive
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/7722—Line condition change responsive valves
    • Y10T137/7837—Direct response valves [i.e., check valve type]
    • Y10T137/7904—Reciprocating valves
    • Y10T137/7908—Weight biased
    • Y10T137/7909—Valve body is the weight
    • Y10T137/791—Ball valves

Definitions

  • the invention relates to a check valve and to an injector.
  • check valves are well known from the prior art. These check valves typically have a valve housing, in which a bore is made, and a valve seat is embodied in the bore. These check valves furthermore have a spherical valve member, which is disposed in the bore, and a stroke stop element for the valve member is provided, on which the valve member comes to rest when the check valve is open.
  • check valves are suitable for many applications, but particularly in use in injectors with a hydraulic pressure booster, of the kind used in modern fuel injection systems for internal combustion engines, applications exist in which the conventional check valves have proven insufficiently durable.
  • the lateral deflection of the valve member in the open position of the check valve has the effect that not until the valve member meets the valve seat is the valve member centered again by the valve seat. This leads to a relative motion between the valve member and the valve seat. This relative motion causes wear and shortens the service life of the valve seat and valve member considerably.
  • the check valve of the invention has the advantage that the valve member in the open state is centered in the indentation in the stroke stop element, and as a result, the valve member of the check valve of the invention strikes the valve seat precisely centrally when the check valve closes again, so that no significant wear between the valve seat and the valve member can be found.
  • a valve spring can be dispensed with, which reduces the production costs and space required for the check valve of the invention considerably. Because of the reduced masses, this check valve responds especially fast. Because of the at least indirect axial fixation of the stroke stop element by means of a welded connection, no additional component is required for this, and as a result the production costs and space required for the check valve of the invention are likewise reduced.
  • At least one transverse bore is provided in the stroke stop element, and the transverse bore connects an annular gap between the stroke stop element and the bore with a longitudinal bore in the stroke stop element.
  • the longitudinal bore is preferably embodied as a throttle bore toward the indentation, and the transition from the indentation to the throttle bore is embodied with sharp edges, in order upon opening of the check valve to damp the motion of the valve member before it strikes the stroke stop element.
  • the transition from the throttle bore to the region of the longitudinal bore remote from the indentation, by comparison, is embodied in streamlined fashion, to enable a rapid lifting of the valve member from the stroke stop element upon closure of the check valve.
  • the check valve of the invention can be used especially advantageously in an injector with a hydraulic pressure booster for an internal combustion engine.
  • FIG. 1 is a longitudinal section through one exemplary embodiment of a check valve of the invention.
  • FIG. 2 is an injector of the invention with a hydraulic pressure booster and a check valve of the invention.
  • a component which may for instance be a pressure booster piston of a hydraulic pressure booster, is identified by reference numeral 1 .
  • this component 1 there is a check valve, described in further detail hereinafter, and the component 1 forms a valve housing for the check valve.
  • a stepped bore 3 is provided in the valve housing 1 .
  • a valve seat 5 is embodied between two portions of the bore 3 that have different diameters.
  • An at least approximately spherical valve member 7 is disposed in the bore 3 .
  • the valve member 7 cooperates with the valve seat 5 in the valve housing 1 and closes the check valve as soon as the valve member 7 rests on the valve seat 5 .
  • the bore 3 Adjoining the valve seat 5 , the bore 3 has a portion 3 a with a diameter that is somewhat greater than the diameter of the valve member 7 .
  • the bore 3 is open and has a portion 3 b with a greater diameter compared to the portion 3 a . Because of the change in diameter from the portion 3 a to the portion 3 b, an annular shoulder 10 facing away from the valve seat 5 is formed in the bore 3 .
  • a stroke stop element 12 is inserted into the bore 3 , from an open end of the valve housing 1 .
  • the stroke stop element 12 has a stepped diameter and has a portion 12 a , disposed in the portion 3 a of the bore 3 , whose diameter is somewhat smaller than the diameter of the portion 3 a of the bore 3 , so that there is an annular gap 14 between the portion 12 a of the stroke stop element 12 and the portion 3 a of the bore 3 .
  • the stroke stop element 12 furthermore has a portion 12 b , disposed in the portion 3 b of the bore 3 , with a greater diameter compared to the portion 12 a .
  • the diameter of the portion 12 b of the stroke stop element 12 is only slightly less than the diameter of the portion 3 b of the bore 3 .
  • an annular shoulder 13 facing toward the valve seat 5 is formed on the stroke stop element.
  • a funnel-shaped indentation 16 is made, which is embodied for instance as approximately frustoconical or domelike.
  • the diameter of the indentation 16 is less than the diameter of the valve member 7 , so that the valve member 7 can dip partway into the indentation 16 .
  • the indentation 16 is disposed at least approximately coaxially to the longitudinal axis 4 of the bore 3
  • the valve member 7 is disposed at least coaxially in the bore 3 and is movable in the direction of the longitudinal axis 4 .
  • a continuous longitudinal bore 20 with a multiply graduated diameter is made in the stroke stop element 12 and discharges on one end into the indentation 16 and on the other at the open end of the bore 3 on the stroke stop element 12 .
  • the longitudinal bore 20 In its region extending toward the indentation 16 , the longitudinal bore 20 has a small diameter and thus forms a throttle bore 20 a .
  • An orifice 20 b of the longitudinal bore 20 into the indentation 16 has a substantially greater diameter than the throttle bore 20 a .
  • the transition from the orifice 20 b into the throttle bore 20 a is abrupt and is embodied with sharp edges, so that the flow, beginning at the indentation 16 , into the throttle bore 20 a is severely hindered.
  • the throttle bore 20 a is adjoined, on its side remote from the indentation 16 , by a further region 20 c of the longitudinal bore 20 , which has a greater diameter than the throttle bore 20 a .
  • the transition from the region 20 c of the longitudinal bore 20 to the throttle bore 20 a is embodied in streamlined fashion; for instance, as shown in FIG. 1 , an approximately conical or rounded transition is provided.
  • At least one transverse bore 22 is made in the portion 12 a of the stroke stop element 12 , and through this transverse bore, the region 20 c of the longitudinal bore 20 is in communication with the annular gap 14 .
  • a plurality of transverse bores 22 distributed over the circumference, are provided in the stroke stop element 12 .
  • the stroke stop element 12 is preferably made from hardened steel, to assure low wear, since when the check valve opens, the valve member 7 strikes the stroke stop element 12 .
  • the valve member 7 is likewise preferably made from hardened steel; conventional balls for ball bearings, which are available as standard parts, can for instance be used as the valve member 7 .
  • the funnel-shaped indentation 16 By means of the funnel-shaped indentation 16 , the valve member 7 is centered in its reciprocal motion, and as a result it is attained that upon its closing motion, the valve member 7 strikes the valve seat 5 at least approximately centrally, so that the wear to the valve seat 5 can be kept low as well.
  • the orifice 20 b of the longitudinal bore 20 in the indentation 16 in the stroke stop element 12 is closed by the valve member 7 .
  • An outflow of fluid is made possible by the annular gap 14 , the at least one transverse bore 22 , and the longitudinal bore 20 in the stroke stop element 12 .
  • the positive displacement of fluid from the indentation 16 into the longitudinal bore 20 is made more difficult, and there is increased flow resistance there.
  • the valve member 7 Upon opening of the check valve, the valve member 7 enters into the indentation 16 and positively displaces fluid from it into the longitudinal bore 20 .
  • the valve member 7 Upon installation of the check valve in the valve housing 1 , the valve member 7 is first introduced into the bore 3 . Next, the stroke stop element 12 is inserted from the open side of the valve housing 1 into the bore 3 , in the direction of the longitudinal axis 4 , until the annular shoulder 13 of the stroke stop element 12 comes into contact with the annular shoulder 10 of the valve housing 1 . The maximum stroke of the valve member 7 that the valve member can execute between its contact with the valve seat 5 and with the stroke stop element 12 is fixed by the axial position of the stroke stop element 12 .
  • the stroke stop element 12 is fixed at least indirectly in the axial direction in the bore 3 of the valve housing 1 by means of a welded connection.
  • the stroke stop element 12 itself is joined by material engagement on its circumference to the valve housing 1 by means of a welded connection 26 in the bore 3 , as shown in the upper half of FIG. 1 .
  • the check valve is disposed near the open end of the valve housing 1 .
  • a welded ring 28 is inserted, by which the stroke stop element 12 is fixed in the axial direction and which is joined by material engagement to the valve housing 1 by means of a welded connection 30 .
  • FIG. 2 an example of the use of the check valve of the invention is shown schematically.
  • An injector is identified in its entirety by reference numeral 55 .
  • the injector 55 is supplied with fuel at high pressure from a common rail 57 via a high-pressure line (not identified by reference numeral).
  • a hydraulic pressure booster 59 is provided in the injector 55 .
  • the hydraulic pressure booster 59 includes a booster piston 61 , which divides a low-pressure chamber 63 from a high-pressure chamber 65 .
  • In the booster piston 61 there is a longitudinal bore 3 .
  • In the bore 3 there is a check valve 67 , shown in stylized fashion, which prevents fuel from being able to flow out of the high-pressure chamber 65 into the low-pressure chamber 63 .
  • This check valve 67 is a check valve in accordance with the exemplary embodiment of FIG. 1 described above.
  • the high-pressure chamber 65 communicates hydraulically with a drum 69 in which a nozzle needle 71 is disposed. Via a first magnet valve 73 , which is embodied as a 3/2-way valve and which controls the hydraulic pressure booster 59 , and a second magnet valve 75 , which controls the pressure in the drum 69 , the nozzle needle 71 is opened and closed.
  • the booster piston 61 is preferably made from a roller bearing steel having a carbon content of approximately 1%.
  • the booster piston 61 is guided with very little play and has a wear protection layer on its outer surface.
  • the heat input into the booster piston 61 in the production of the welded connection 26 , 30 for fixation of the stroke stop element 12 in the bore 3 of the booster piston 61 must therefore be kept as slight as possible.
  • the guidance play of the booster piston 61 and damage to the wear protection layer of the booster piston 61 from thermal factors in welding and/or thermal warping is minimized, and subsequent overly slight guidance play of the booster piston 61 and accordingly increased wear is avoided.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Check Valves (AREA)
  • Fuel-Injection Apparatus (AREA)
US12/520,136 2007-01-17 2008-01-02 Check valve, and injector with hydraulic booster and check valve Expired - Fee Related US7789069B2 (en)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
DE102007002445 2007-01-17
DE102007002445.4 2007-01-17
DE102007002445A DE102007002445A1 (de) 2007-01-17 2007-01-17 Rückschlagventil und Injektor mit hydraulischem Übersetzer und Rückschlagventil
PCT/EP2008/050016 WO2008087051A1 (de) 2007-01-17 2008-01-02 Rückschlagventil und injektor mit hydraulischem übersetzer und rückschlagventil

Publications (2)

Publication Number Publication Date
US20100024774A1 US20100024774A1 (en) 2010-02-04
US7789069B2 true US7789069B2 (en) 2010-09-07

Family

ID=39301163

Family Applications (1)

Application Number Title Priority Date Filing Date
US12/520,136 Expired - Fee Related US7789069B2 (en) 2007-01-17 2008-01-02 Check valve, and injector with hydraulic booster and check valve

Country Status (6)

Country Link
US (1) US7789069B2 (ja)
EP (1) EP2126427B1 (ja)
JP (1) JP5135355B2 (ja)
AT (1) ATE536507T1 (ja)
DE (1) DE102007002445A1 (ja)
WO (1) WO2008087051A1 (ja)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20100076471A1 (en) * 2008-09-25 2010-03-25 Bourne John M Spring-Less Check Valve For A Handpiece
US20140361096A1 (en) * 2013-06-11 2014-12-11 Cummins Inc. System and method for control of fuel injector spray
US20150267631A1 (en) * 2013-03-22 2015-09-24 Kawasaki Jukogyo Kabushiki Kaisha Fuel supply controlling device for divided-chamber gas engine
US11339688B2 (en) 2020-01-29 2022-05-24 Borgwarner, Inc. Variable camshaft timing valve assembly

Families Citing this family (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2746566A1 (en) * 2012-12-18 2014-06-25 Delphi International Operations Luxembourg S.à r.l. Pump Unit
DE102013209204A1 (de) 2013-05-17 2014-11-20 Robert Bosch Gmbh Rückschlagventil
DE102018131094A1 (de) 2018-12-06 2020-06-10 Schaeffler Technologies AG & Co. KG Ventil
DE102018131095A1 (de) 2018-12-06 2020-06-10 Schaeffler Technologies AG & Co. KG Ventil und Vorrichtung zur Regelung von Drücken eines Strömungsmittels mit dem Ventil sowie Vorrichtung zur Sicherung des Ventils in dem Getriebebauteil
DE102018131097A1 (de) 2018-12-06 2020-05-14 Schaeffler Technologies AG & Co. KG Vorrichtung zur Sicherung eines Druckausgleichsventils in einem Getriebebauteil, Druckausgleichsventil und Vorrichtung zur Regelung von Drücken eines Strömungsmittels in einem Fahrzeuggetriebe
DE102019120227A1 (de) 2019-07-26 2020-08-06 Schaeffler Technologies AG & Co. KG Ventil und Vorrichtung zur Regelung von Drücken eines Strömungsmittels mit dem Ventil sowie Vorrichtung zur Sicherung des Ventils in dem Getriebebauteil
DE102019120225A1 (de) 2019-07-26 2021-01-28 Schaeffler Technologies AG & Co. KG Ventil und Vorrichtung zur Regelung von Drücken eines Strömungsmittels mit dem Ventil sowie Vorrichtung zur Sicherung des Ventils in dem Getriebebauteil
DE102019120226A1 (de) 2019-07-26 2020-08-06 Schaeffler Technologies AG & Co. KG Ventil und Vorrichtung zur Regelung von Drücken eines Strömungsmittels mit dem Ventil sowie Vorrichtung zur Sicherung des Ventils in dem Getriebebauteil
DE102019120224A1 (de) 2019-07-26 2020-08-06 Schaeffler Technologies AG & Co. KG Ventil und Vorrichtung zur Regelung von Drücken eines Strömungsmittels mit dem Ventil sowie Vorrichtung zur Sicherung des Ventils in dem Getriebebauteil
DE102019132416B4 (de) * 2019-11-29 2022-02-10 Schaeffler Technologies AG & Co. KG Ventil und Vorrichtung zur Regelung von Drücken eines Strömungsmittels mit dem Ventil sowie Vorrichtung zur Sicherung des Ventils in dem Getriebebauteil
DE102019132415A1 (de) * 2019-11-29 2021-06-02 Schaeffler Technologies AG & Co. KG Ventil und Vorrichtung zur Regelung von Drücken eines Strömungsmittels in einem Fahrzeuggetriebe
DE102020112780A1 (de) 2020-05-12 2021-11-18 Schaeffler Technologies AG & Co. KG Druckausgleichsventil und Getriebeanordnung mit Druckausgleichsventil

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US3939869A (en) * 1972-08-30 1976-02-24 Sterling Hydraulics Limited Hydraulic control valve for remote receiver
EP0268520A2 (fr) 1986-11-06 1988-05-25 Automobiles Peugeot Clapet anti-retour pour circuit de liquide sous pression dans un moteur à combustion interne
US4945945A (en) 1989-11-30 1990-08-07 The Perkin-Elmer Corp. Check valve assembly for corrosive fluids
DE4203161A1 (de) 1992-02-05 1993-08-12 Werner Karl Heinz Dipl Ing Hydraulisches rueckschlag- oder ueberstroemventil
DE19501725A1 (de) 1994-02-15 1995-08-17 Barmag Barmer Maschf Rückschlagventil insbesondere für Kunststoffschmelzen
GB2287085A (en) 1994-03-05 1995-09-06 Actis Non-return valve
US5791374A (en) * 1995-12-07 1998-08-11 Black; Art Check valve for the pre-combustion chamber of an internal combustion engine
US6029685A (en) 1999-01-15 2000-02-29 Carruth; Don Vernon Cage assembly for ball check valves
US20040055580A1 (en) * 1999-02-09 2004-03-25 Hitachi, Ltd. High pressure fuel supply pump for internal combustion engine
US20060005815A1 (en) * 2002-10-10 2006-01-12 Hans-Christoph Magel Filter arrangement for fuel injection systems
WO2007057255A1 (de) 2005-11-21 2007-05-24 Robert Bosch Gmbh Rückschlagventil und injektor mit hydraulischem übersetzer
DE102006010706A1 (de) 2006-03-08 2007-09-13 Schaeffler Kg Ventil für strömende Medien

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JPS60129566U (ja) * 1984-02-10 1985-08-30 株式会社小松製作所 逆止弁
JPS6435181A (en) * 1987-07-29 1989-02-06 Nippon Denso Co Check valve
JPH0377009U (ja) * 1989-11-29 1991-08-01
JP2604355Y2 (ja) * 1993-12-29 2000-05-08 松本重工業株式会社 チェックバルブ
US5533548A (en) * 1995-05-18 1996-07-09 Caterpillar Inc. Valving interface for a poppet valve
DE19950224A1 (de) * 1999-10-19 2001-04-26 Bosch Gmbh Robert Doppelschaltendes Steuerventil für einen Injektor eines Kraftstoffeinspritzsystems für Brennkraftmaschinen mit kugelförmigem Stellglied
EP1613856B1 (de) * 2003-04-02 2008-07-09 Robert Bosch Gmbh Servoventilangesteuerter kraftstoffinjektor mit druckübersetzer
DE102004053421A1 (de) * 2004-11-05 2006-05-11 Robert Bosch Gmbh Kraftstoffeinspritzvorrichtung

Patent Citations (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3939869A (en) * 1972-08-30 1976-02-24 Sterling Hydraulics Limited Hydraulic control valve for remote receiver
EP0268520A2 (fr) 1986-11-06 1988-05-25 Automobiles Peugeot Clapet anti-retour pour circuit de liquide sous pression dans un moteur à combustion interne
US4945945A (en) 1989-11-30 1990-08-07 The Perkin-Elmer Corp. Check valve assembly for corrosive fluids
DE4203161A1 (de) 1992-02-05 1993-08-12 Werner Karl Heinz Dipl Ing Hydraulisches rueckschlag- oder ueberstroemventil
DE19501725A1 (de) 1994-02-15 1995-08-17 Barmag Barmer Maschf Rückschlagventil insbesondere für Kunststoffschmelzen
GB2287085A (en) 1994-03-05 1995-09-06 Actis Non-return valve
US5791374A (en) * 1995-12-07 1998-08-11 Black; Art Check valve for the pre-combustion chamber of an internal combustion engine
US6029685A (en) 1999-01-15 2000-02-29 Carruth; Don Vernon Cage assembly for ball check valves
US20040055580A1 (en) * 1999-02-09 2004-03-25 Hitachi, Ltd. High pressure fuel supply pump for internal combustion engine
US20060005815A1 (en) * 2002-10-10 2006-01-12 Hans-Christoph Magel Filter arrangement for fuel injection systems
WO2007057255A1 (de) 2005-11-21 2007-05-24 Robert Bosch Gmbh Rückschlagventil und injektor mit hydraulischem übersetzer
DE102006010706A1 (de) 2006-03-08 2007-09-13 Schaeffler Kg Ventil für strömende Medien

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20100076471A1 (en) * 2008-09-25 2010-03-25 Bourne John M Spring-Less Check Valve For A Handpiece
US8291933B2 (en) * 2008-09-25 2012-10-23 Novartis Ag Spring-less check valve for a handpiece
US20150267631A1 (en) * 2013-03-22 2015-09-24 Kawasaki Jukogyo Kabushiki Kaisha Fuel supply controlling device for divided-chamber gas engine
US9816449B2 (en) * 2013-03-22 2017-11-14 Kawasaki Jukogyo Kabushiki Kaisha Fuel supply controlling device for divided-chamber gas engine
US20140361096A1 (en) * 2013-06-11 2014-12-11 Cummins Inc. System and method for control of fuel injector spray
US9562505B2 (en) * 2013-06-11 2017-02-07 Cummins Inc. System and method for control of fuel injector spray
US11339688B2 (en) 2020-01-29 2022-05-24 Borgwarner, Inc. Variable camshaft timing valve assembly

Also Published As

Publication number Publication date
JP5135355B2 (ja) 2013-02-06
EP2126427B1 (de) 2011-12-07
DE102007002445A1 (de) 2008-07-24
WO2008087051A1 (de) 2008-07-24
JP2010516932A (ja) 2010-05-20
ATE536507T1 (de) 2011-12-15
US20100024774A1 (en) 2010-02-04
EP2126427A1 (de) 2009-12-02

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